Pump



Nov. 22, 1932.

C. B. SANDERS- PUMP Filed Dec. 22, 1928 NVENT% kw 9 Sheets-Sheet l ATTORNEY Nov. 22, 1932.

c. B. SANDERS PUMP Filed Dec. 32, 1928 9 Sheets-Sheet 3 IIIIIIIIIIIIIIIIIIIIIIIIIII 'IIIIIIIIIIIIIIIIIIIII IIIllIIIIIIIIIIIIIIII'll!IIIIIIIIIIIIIIIIIIII a w INVENTOR 42% W ATTORNEY Nov. 22,1932.

c. B. SANDEiQS PUMP ' Filed Dec. 22, 1928 9 Sheets-Sheet 4 c. B. SANDERS PUMP Filed Dec. 22, 1928 9 Sheets-Sheet 5 Nbv. 22, 1932.

Nov. 22, 1932. c. B. SANDERS,

PUMP

9 Sheets-Sheet 6 Filed Dec. 22, 1928 ATTORNEY Nov. 22, 1932. c. B. SANDERS PUMP Filed Dec. 22, 1928 9 Sheets-Sheet 7 mum-1 Nov. 22, 1932. c'. B. SANDERS 1,888,474

' PUMP Filed Dec. 22, 1 928 9 Sheets-Sheet 8 NOV. 22, Q 5 SANDERS PUMP Filed Dec. 22, 1928 9 Sheets-Sheet 9 Patented Nov. 22, 1932 TTS CRAWFORD B. sAivnEns, or wYAnno'rTE, MICHIGAN PUMP Application filed December 22, 1928. Serial No. 327,951.

My invention relates to lubricators and more particularly relates to lubricator pumps for providing forced lubrication in regulated quantities to various points. 7

Many machines in use today have a plurality of bearings each of which require more or less lubricant, dependent upon the amount of work that the particular bearing is called upon to do. Providing the required amounts of lubricant to the various bearings without within the oil reservoir.

Another object of my invention is to provide a force feed lubrication pump wherein the amount of lubricant supplied to separate bearin s ma 1 be ad 'usted to su lv various quantities of oil to the different bearings.

Another object of my invention is to pro vide a pump for supplying various amounts of liquids to various points wherein the jamount of'liquid to each point may be independently adjusted relative to the other points.

Another object of my invention is to provide a lubricator of the-class described which .may be readily dismounted for repairs and wherein the outer shell or case may be left upon the machine and the mechanism quickly replaced by another.

Another object of my invention is to provide a lubricator of the class described'which has no springs, in the same.

Another object of my invention is to provide a device of the class described wherein the location of the initial drive eliminates the use of numerous packings and which eliminates the possibility of fluid leakage.

Another object of my invention is to provide a device of tee class described which is compact and requires a minimum amount of space in which to set the same.

Another object of my invention is to provide a lubricating device of the class described which may be adjusted to vary the amounts of liquid supplied, while the pump is in operation.

Another object of my invention is to provide a lubricating device of the class described wherein the pump may be combined with the oil reservoir or wherein the reservoir may be separ ted and remote from'the pump.

Another object of my invention is to provide a novel mechanical movement which may be advantageously made of wid application.

Another object of my invention is to provide a lubricating pump which may be operated from a revolving shaft or from an eccen trio without materially changing the mechanism of the device. 1

Another object of my invention is to pro vide a device of the class described which is easy and economical to manufacture and which is simple in operation and adjustment. Another object of my invention is to provide a lubricator having sleeve valves and pistons operated by a common crank.

Another object of m invention is to provide a lubrication device wherein the volume output depends upon the relative movement of the piston and sleeve;

Another object of my invention is to provide a lubricating device having sleeves and. pistons operative from a common source of power wherein the relative movement of the sleeves and pistons may be varied.

Another object of my invention is to pro vide a lubricator having sleeve valves and cooperating pistons, wherein the travel of one element remains constant and the travel of the other element may be varied.

Another objectof my invention is to provide a device of the class described wherein the cylinder and piston therefor may both be operated from a common crank at relatively variable speeds.

@ther objects and the invention itself will become apparent from the following descrip- I tion of an embodiment thereof in which description reference will be had to the accom panying drawings illustrating the said em bodiment and forming a part of this specification.

Referring to the drawings:

F i 1 is a vertical sectional view taken on the line 11 of Fig. 4, a part thereof being broken away;

Fig. 2 is a. view taken on the line 2-2 of Fig.2? is a vertical sectional View taken on the line 3-3 of Fig. 4;

Fig. 4 is a plan view, certain parts being broken away and shown in section;

Fig. 5 is a relatively enlarged fragmentary sectional view of one of the pumping elements and actuating mechanism therefor;

Fig. 6 is a diagrammatical View showing a method of rating the device;

Figs/7 an 9 are isometric views of the two clevises used;

Fig. 8 is a perspective view of one of the eccentric cam elements;

Fig. 10 is a view similar to F ig. 2, of run other embodiment of my invention;

Figs. 11, 12 and 13 are diagrainmatical views illustratin the orbits of travel of the piston and cylinder operating links;

Fig. 14 is a fragmentary vertical sectional view of another drive for my device; and

Fig. 15 is a view on the line 15-15 of Fig. 14.

eferring to the figures of the drawings wherein like parts are designated by like reference characters, my device comprises generally, a casting 2, which supports the pumping mechanism, and a sheet metal housing or tank 3 into which the lower part of the casting is adapted to set, and which in some instances may act as a reservoir.

The tank or housing 3 may be made in two arts, as illustrated, the sides 4, supporting a ottom portion the sides of the bottom portion being telescoped snugly within the sides 4 and welded or otherwise secured thereto, forming a fluid tight box. The opposite sides 6 and 7 of the bottom are strengthened by struts 8 and the upper edges 9 and of the sides are inturned to form a short flange which extends longitudinally along the two sides of the housing and serves as a stop for the adjustment mechanisms later described. The pumping mechanism is driven by means ofa driven flan e 11, which is rotatably journalled by its ub in a bearing supported by the casting 2, and has a shaft 12 keyed therein relatively immovable to the flange, by a suitable key 13. The shaft and key are relatively long and extend rearward from the driven flange, the end of the shaft being supported by a bearing 14 disposed in a recess 16 in the casting- The shaft is retained within the bearing by a ring 17 pinned to the shaft by a taper pin 18, suitable apertures 19 and 20 being provided for removing and applying said pin.

A. pawl wheel 21 which has a relatively long axial boss 22 is also keyed to the shaft 12, by the extended key 13, intermediate the driven flange and the bearing 14; it is adapted to carry swivelled thereon pawls 23, 24, 25 and 26 upon equally spaced radially disposed pins 27. The axial boss 22 of the pawl wheel is adapted to carry rotatably journalled thereon a driven gear 28 which is provided with a ratchet wheel 29 secured upon an axial boss of the driven gear relatively immovably thereon by pins 30.

The awls are adapted to beheld in spring pressed engagement with the teeth of the ratchet wheel 29 by means of a resilient metallic ring 31 which encircles all of the pawls; the inner wall thereof contacting with the pawls adjacent their ends.

The relative positions of the pawls and the teeth'on the ratchet wheel is such that only one pawl is in engagement with the bottom of the notch formed by the tooth; each of the other pawls being progressively further advanced upon its respective tooth; the pawl 23 being shown fully engaged with the tooth while the pawl 24 is removed approximately one quarter the distance of the tooth respectively.

With the pawls arranged as described the amount of backward movement of the ratchet is minimized as the relative movement of the ratchet gear and pawls need be only one fourth the length of the tooth for the next succeeding pawl to engage a notch of a tooth.

As before stated the ratchet gear is relatively immovably secured upon the hub'of the driven gear 28, which is rotatably journalled upon the axial boss or hub 22 of the pawl wheel. Longitudinal axial movement of the ring 31 is prevented by reason of its location between the flanges of the pawl wheel and the driven gear.

The teeth of'the driven gear 28 mesh with the teeth of a crank shaft gear 32 which is rotatably journalled in a bearing 33 by hub 34, said bearing being held hya downwardly extending web 35 of the casting 2.

The hub of the gear 32 is provided with an eccentric longitudinal bore 36. One end of a crank 37 is relatively immovably keyed in the bore 36 by a suitable key 38, and is adapted to drive the pumping elements. The other end of the crank 37 is provided with an eccentric annulus 39 keyed upon the crank by a suitable key 40, the periphery of said annulus being in alignment at all points with the periphery of the hub or axial projection 34 of the main shaft gear 32, the assembly acting as a shaft and crank.

Said annulus is rotatably ournalled. in the bearing 41 which is supported by a bearing support 42 at the lower end of a web 43 similar to the support for gear hub.

Rotational or oscillatory movement imparted to the driven shaft flange 11 by a rotating shaft or by an eccentric linkage 11', as shown in Fig. 6, will transmit like movement to the shaft 12 and thence to the wheel 21 through the pawls to the ratchet and driven gear 28 imparting rotational movement to the gear 32. Rotation of the gear 32 transmits a rotational eccentric movement to the crank 33'? which operates the sleeves and pistons as later described.

In the embodiment illustrated, I have shown a lubricator which has twelve pumping elements, the pumping elements being placed in two rows of six each. It is within the purview of my invention, however, to make lubricators in various combinations, from those embodying a single pump to those having aplurality of pumps,dependent upon the demand to be made of the device.

As previously stated, the mechanism is mostly carried by the casting 2. Said casting is of generally rectangular plan and carries at one end an upwardly extending housing 44 which houses the ratchet mechanism de- I the crank 37.

scribed. The extreme upper end of the housing 44 is open and is separated from the intermediate ratchet housing proper by an arcuate wall 45 thus producing a chamber 46 above the ratchet mechanism. A screen is provided at 47 and a cover 48 is placed above the screen, both elements being secured to the housing by screws 49.

An aperture 50 inthe cover is adapted to provide an inlet means for the oil from a tank, not shown. The oil, being strained by the screen 47, (descends into the oil chamber 46 where it is conducted by conduits 151 which connect with the lower part of the chamber 46, into'inlet ducts or canals 52, extending longitudinally on each side of the casting adjacent each set of pumps.

Each pump element comprises generally a reciprocable piston and cylinder operating through a cylindrical aperture in the casting, by eccentric connecting links ournalled upon A description of one pumping element will sufiice for all.

The piston 51 may be made of a solid piece of drill rod or like material, of cylindrical form, and is provided with a lower exteriorly threaded reduced end 52. The end 52 is adapted to be engaged by the externally threaded end 58 of a clevis or cross head 54. The other end of the clevis is provided with oppositely disposed axially aligned apertures 55 adapted to secure the clevis to the small end of a connecting link 56 by a suitable pin 57 which extends through the apertures 55 of the clevis and 58 of the link, the ends of the pin 57 being flush with the sides of the clevis.

The connecting link 56 is generally ovate shaped, the enlarged end being provided with an aperture 59 of suflicient size to allow the link to oscillate freely upon the crank 87. The eccentric revolving movement of the crank 37 reciprocates the link 56 and the piston 51 connected thereto.

The cylinder 60 may also be made from drill rod or other suitable material, and is substantially larger than the piston being provided with a longitudinal bore 61 extending partially therethrough, of size sufiicient to receive the, piston therein; the end 62 remote from the drive shaft, being closed.

The cylinders are adapted to reciprocate in cylindrical guideways 63 which in this instance set at an angle of approximately 30 displaced from the vertical, adjacent the canals 52. The wall 64 separating the guideway from the canal 52 is relatively thin. The upper end of the cylinder projects through the guide into the upper portion 65 of the casting, which is open to the lower portion of the device preventing any back pressure-which might be otherwise set up by the reciprocating cylinder. I

An inlet port 66 is provided in the cylinder, and is adapted to register at a predetermined point with a corresponding inlet port 67, in the wall 64, which connects with the canal 52. An exhaust port 68 in the opposite side of the cylinder wall is adapted to register in a similar manner with the exhaust canal 69.

The inlet port 67 is constructed by drilling through the walls and 64 of the casting and closing the aperture in the wall 70 with a plug 71.

The exhaust canal 68 is constructed similarly by drilling through the walls 70 and 64 into the wall 72 and then drilling from the upper end of the casting downward to meet the canal 68, after which the apertures in the walls 70 and 64 are closed by a single plug 73.

The lower end of the cylinder is reduced and exteriorly threaded at 74, and is adapted to be engaged by the internal threads 7 5 of a clevis or cross head 7 6. The clevis 76 is suiiiciently large to encompass the clevis 54 there being sufiicient clearance between the two clevis es to allow the arms 77 and 78 of a pair of cylinder operating links 81 and 82 to be pivotally held therebetween by a pair of short cylindrical pins 79 which are insorted in oppositely disposed aligned apertures in the clevis and links.

The links 81 and 82 are shaped similar to the link 56 but are relatively large and their small ends 7 8 and 79 are offset at 83 and 84 to allow the clevis 54 to reciprocate freely therebetween. The enlarged ends of the links have relatively large aligned circular apertures 85 and 86 adapted to be journalled upon a171 eccentric cam 87 disposed upon the crank 3 ltll) The eccentric cam 87, as best shown in Fig. 8, comprises a pair of circular metallic discs 88 and 89, spaced from each other by a generally Y-shaped control yoke 90. The discs being secured to each side of the yoke 90 by rivets 91. Axially-aligned apertures 92 and 93 are provided in the discs eccentric from the center thereof and are ada ted to engage the crank 37 to rotate freely t iereon.

The large apertures 85 and 86 in the links 81 and 82 are adapted to engage the periphcries of the discs 87 and 89 of the cam element; the piston link 56 being adapted to fit freely between the discs 88 and 89 upon the crank 37.

As best shown in Fig. 3, the end 94 of the control yoke 90, is secured to one end of a link 95 which has the other end connected to the lower end 96 of an adjusting element.

The adjusting element comprises a sleeve 7 96 which has external left hand threads, and

is disposed in the enlarged threaded end 97 of a vertical aperture 98, which is located adjacent the side of the casting and the canal 52. The sleeve 96 is provided with double right hand internal threads 99 adapted to engage the reduced threaded end 100 of a rod 101. The rod is provided with a clevis 96 at its lower end and the end of the link 95 is pivotall held therein by a pin 102.

The upper end of the sleeve 96 is provided with a transverse slot 103 adapted to be engaged by a wrench or screw driver to rotate the sleeve by screwing it downward or upward which causes the rod 101 with the double right hand threads to travel downward at a greatly increased speed dependent upon the pitch of the threads. V rtical adjustment of the rod 101 changes the relative position of the link 95 to vary the arcuate path of travel of the end 93 of the eccentric cam.

That portion of each piston link and cylinder assembly adjacent the crank 37, as viewed in Figs. 1 and 5 is of such dimension as to be one half of that of the portions adjacent the clevises. The portions near the clevises including the pins 79 and 57 and the surfaces of the clevises, contact with every other assembly at that point; the portions adjacent the crank 37 contact with the adjacent assembly. This allows every adjacent assembly to extend angalarly relative thereto and still retain the parts in their respective operative positions. A pair of apertures are provided with plugs 134 and 135 screw threaded therein in the end of the casting, and align with the pins 7 9 and 57, to provide a means to gain access thereto for assembly purposes and the like, and adapted to abut the pin 79 and cross head 76 in the end element to hold the pins in their relatively operable position.

The cam element 87 being journalled directly upon the crank 37, travels with said cranks circular orbit. The orbit, however, of the axis of the cam element is not circular but is elliptical due to the changing ofthe relation of the axis of the cam and the shaft, during rotation of the shaft. The end 94 of the control yoke, being held by the link 95, will be allowed movement only in the radius described by the end of said link which is pivoted at 102.

The links 81 and 82 being journalled upon the peripheries of the discs 88 and 89 are also carried in the elliptical orbit by said cam 87.

When the device is put into operation,the fluid, such as oil, is supplied by a conduit from a tank, not shown, to the inlet aperture in the top of the casting. The oil passes down through the screen 47 into the chamber 46, and is then conducted by conduits 51 to the inlet canals 52 disposed on each side of the casting. It is then sucked into the cylinder 61 through the inlet ports 66 and 67 at the lower portion of the piston and cylinder stroke cycle and on the upward portion of the cycle it is forced out of the cylinder through the exhaust portion 68 into the exhaust canal 69.

It is then conducted through suitable conduits to the various points of application. The conduits being attached to the canals 69 by suitable nipples threaded into the threaded apertures disposed in the top of the casting as best shown by Fig. 1.

The pumping action is due to the relative differences in rates of movement of the piston and cylinder which occurs when the inlet or exhaust ports register with the cylinder inlet or exhaust ports, and which is best described by reference to Figs. 11, 12, and 13.

Fig. 11 shows diagrammatically the slanting bore or guide 63, in which the cylinder 60 reciprocates; the piston 51 being disposed in the bore of the cylinder and the piston and cylinder being connected to the links 56 and 82 as previously described, the various parts being shown as in aposition adjusted for pumping. The dotted circle 104 represents the rotational eccentric orbit through which the center 105 of the crank 37 revolves, and which is, therefore, the orbit of travel of the crank end of the link 56 which encircles the crank. The link being rotatably ournalled upon the crank acts as a connecting rod and reciprocates the piston. The longitudinal movement transmitted to the piston 'will be the same for each succeeding cycle, and is best illustrated by Fig. 12, which is an enlarged view of the orbits of the piston and cylinder operating elements.

The line aiy is drawn along the longitudinal axis of the piston and intersects the axis of the orbit 104, which orbit always remains in the same position. The lines A to X inelusive, are projected from twenty-five equally spaced points about the orbit 101 letter a to m, and intersect the line aa I which is parallel to the line m7 The center of the shaft having traveled from a to Z), the longitudinal travel of the piston will be the distance AB which is relatively small. The longitudinal movement of the piston will vary with that of the circular movement of the orbit depending upon that portion of the 5 to the center of rotation of the crank. The

orbit through which the movement is being transmitted, that is at the A-B movement of piston, the movement is relatively small compared with the distance a-Z9 that the center of the crank travels about. However when the center of the crank reaches the point fg and g-h the movement of the piston is F-G and G-H and the longitudinal distance traveled by the piston most nearly equals the distance traveled by the center of the crank through the orbit, and so on throughout the complete cycle of the piston and connecting link 56.

The longitudinal movement of the cylinder, however, is quite different, due to the fact that the orbit traveled by the axis of the enlarged portions of the cylinder links 81 and 82, which encircles the camming discs is not a true circle but is substantially elliptical. This is brought about as follows: the cam element 87, which is rotatably journalled upon the crank 37, has the end of the control yoke 94 attached to a link 95. The other end of the link is pivotally held by the adjustment rod 101, by this arrangement the movement of the end of the control yoke is limited to the arcuate path P-P, described by the end of the link 95, the point 102 acting as the pivot. When the crank37 rotates in its circular orbit the center of the apertures 92 and 93, Fig. 8, also travels in this orbit. These apertures, however, are eccentric to the center'106 of the cam discs 88 and 89 which are, therefore, disposed eccentrically end of the control yoke 9A being held by the link 95 travels in the arcuate path P-P due to the same movement that forces the piston longitudinally. The center of the cam discs will then travel in an elliptical orbit 107 due to the constantly shifting center 106 of the disc, which shifting movement is lateral-relative to the center of the crank. The cyl inder links 81 and 82, being journalled on'the peripheries of the cam discs 88 and 89 will be carried in said elliptical orbit. The ends of the links 81 and 82 being secured to the cross head and thence to the cylinder cause the cylinder to reciprocate longitudinally. The longitudinal movement of the cylinder relative to the longitudinal movement of the piston is best shown by the diagram in Fig. 12. The orbit 107 being divided into twenty- ;(ive equally spaced points designated a" to 00 inclusive. The dotted lines project at right angles from the line wy and intersect the line w;z in a manner similar to that previously described for the orbit of the crank 37, indicate the longitudinal movement of the cylinder by the letters Ato X inclusive.

The travel ofthe cam from a. to b will cause a longitudinal movement of the cylinder from A to B, which distance is longer than that AB described by the piston.

The position of the piston and cylinder being at the top of the stroke, the exhaust ports are aligned. The cylinder traveling faster than the piston reduces the space above the piston forcing some of the fluid out of the exhaust ports. As piston and cylinder continue downward the ditl'erences in movement cease at approximate 90 and both travel at approximately the same rate until they approach the bottom of the stroke wherein the space above the piston will increase causing. a suction to be created which, now that the intake ports are registering, allows a quantit-y of oil to come into the cylinder.

The cycle then continues as described, the position indicated in Fig. 12 being the maximum pumping position attained when the adjustment is at its highest position as indicated by the dotted lines in Fig. 3.

Perhaps the best way to show the pumping action is to take the actual measurements for a given device. The measurement of the space above the piston at the top of the stroke at the point a and a will be taken as standard or zero, and all measurements of the fluid filled space will be the relatively larger or smaller longitudinal measurements indicated by plus or minus.

Starting at the bottom of the stroke at m, the space is found to be .0125; when the piston reaches N and the cylinder is at a, the space will be .0062 and a slight expulsion of fluid will occur through the intake. At 0 and O however, it is found that the space has increased to .0187 resulting in an intake of fluid and then P andP become .0250, Q, and Q, become .03? 5, R and R become .0468 showing a continual expansion or intake; S and S become .0406. Between the points It and S the intake ports close and the exhaust ports open and expulsion starts due to the reduction in the space above the piston.

T and T become U and U become V and V become W and W become X and X become C and C become -.0125 D and I) become .0312 E and E remain .0312 F andF remain .0312

As the points G and G are reached the exhaust closes and the intake opens, the space above the piston starting to become larger, being .0125 and thus:

H and H remain .0125

I and I become .0062 J and: J become .0062

K and K become .0000 L and L become .0062 M and M become .0125

The 11 ward stroke now starts and N and N show t e measurements before indicated thus completing the cycle.

In the diagram illustrated in Fig. 11, wherein the line ave-y intersects the axis of the orbit 104 and the longitudinal axis of the iston and cylinder; the point A on the orbi 104 being taken as 0 or 360, it is found that the exhaust ports cease to register, closing between f and g at 81 '15 on the downward stroke and that for 4 neither intake or exhaust are open. At 85 15 the intake ports open and continue to remain open for 177 25', closing between 1" and S at262 40, all ports then remain closed for 2 20' after which the exhaust ports open at 265 and remain open until 81 15 is again reached.

It will thus be noted that on the down stroke the piston and cylinder are traveling at practically the same speed when the ports are closed and the same condition exists on the other side on the upward stroke.

When the adjustment is screwed down until the rod 101' strikes the flange 9, the end 94 of the control yoke will: be shifted, as Shown, and the cam elements will be shifted, sothat the elliptical orbit will be in a posi tion relative to the crank orbit wherein the longitudinal axis of the elipse will fall on the same side as the axis of the crank orbit and lon itudinal axis of the piston before describe as the line a; z 'VVhen the piston and cylinder now reach the point wherein the pumping action ordinarily occurs due to the relative differences in movement of pistons and cylinders it will be found that the enlargement of the fluid chamber at the lower portion of the upward stroke is'equalled by the reduction immediately prior thereto on the down stroke, therefore although the in take ort is open the pump will expell before it reaches the bottom just as much as it takes in on the up stroke and no fluid travel will be observed except a slight pulsation. The same applies to the upper or exhaust position where although fluid is expelled on the upward stroke an equal amount is also taken in on the downward stroke before the ports are out of register. 7

Fig. 13 best illustrates this movement wherein the orbits of travel of the piston link and cylinder link, and wherein the longitudinal axis of the elliptical orbit of the cylinder link falls upon the axial line 1 which as previously stated is the line through theaxis of the piston and orbit described by the crank or piston link. This position represents a non-pumping position. Upon the upward stroke of the piston and cylinder it will he noted that an amount of 'oil will be expelled but immediately after adjustment shifts the longitudinal axis of y.

the orbit followed by the cylinder link causing the relative diiferent'movements of the piston and cylinder as previously described.

In Figs. 14 and 15, I have shown another drive for the crank, which passes directly through the end wall of the tank or housing 3. A driven flange 108 is keyed upon a shaft 109 with a key 110; a ring 111 is secured to the tank 3, by rivets 112, aligning with an aperture 113 in the tank. The flange is provided with threaded apertures 11 1 adapted to receive therein bolts 115 to hold a packing gland for the shaft, which comprises a male and female flange 116 and 117, with suitable packing 118interposed between them and surrounding the shaft, to prevent fiuid leakage.

An annular flange'119 is disposed on the shaft at an intermediate portion thereof to take up the thrust, and the other end of the shaft is keyed in a pawl carrier 120 with a key 121. The pawl carrier comprises a hub 122 rotatably journalled in a ratchet wheel 123. An arm 124 extends from the hub 12:

and has pivoted adjacent its end, a pawl 125 by a pin 126. v

The pawl is retained in spring pressed engagement, with teeth 127 on the periphery of the ratchet wheel, by a spring pressed plunger 128 which bears against an angular extension 129 on one end of the pawl.

The ratchet wheel comprises a hub 130 rotatably journalled in a bearing 131 suspended by the web 43. The crank 37 is keyed within an eccentrically disposed aperture 132 in the hub 130. 7

Rotary or oscillatory movement imparted to the driven flange 108 imparts a like movement to the shaft 109 carrying with it the pawl carrier 120, which movement is transmitted to the ratchet wheel 123, retractive movement of the ratchet wheel is prevented by another pawl 133 pivotally secured to the web 43 and which is held in spring pressed engagement with the teeth 127.

Rotational movement thus described by the ratchet wheel imparts an ecentric rotational movement to the crank 37 as described for the other drive mechanism.

In Fig. 10 I have shown another embodiment of my invention wherein the pumping mechanism is similar to that first described. The oil supply may be poured in the top 137, by raising the lid 138 which is hinged at 139. The oil descends through the screen lelO into the bottom 5 of the tank 8, where it may be sucked up by the conduits 1- 11; the conduits being provided with suitable screened suction flanges 142. This provides a means of combining the oil supply with the pump and housing, as distinguished from the embodiment previously described wherein the oil supply is separate therefrom.

Having thus described my invention and a method of operation thereof, I realize that numerous and extensive departures may be made therefrom, but without departing from the spirit of my invention.

I claim:

1. In a pumping mechanism, a cylinder element, a piston element reciprocable there in, said elements being concurrently reciprocable, separate driving means for each said reciprocable element, means connecting both said driving means to effect synchronous operation thereof, one of said driving means adapted to move its associated element at rates both greater and less than the rates at which the other element is concurrently driven by its associated driving means at diiiei ent parts of the cyclic period of reciprocation of said elements, one of said driving means comprising a crank moving eccentrically in a circular path, the other of said driving means comprising a cam rotatably mounted on the crank and constrained to move in an elliptical path, each of said driving means including a driven rod for communicating motion to the associated element.

2. In a pumping mechanism, a cylinder element, a piston elementreciprocable therein, said elements being concurrently reciprocable, separate driving means for each said reciprocable element, means connecting both said driving means to effect synchronous op eration thereof, one of said driving means adapted to move its associated element at rates both greater and less than the rates at which the other element is concurrently driven by its associated driving means at different parts of the cyclic period of reciprocation of said elements, one of said driving means comprising a crank moving eccentricall in a circular path, the other of saiddriving means comprising a cam rotatably mounted on th crank and constrained to move in an elliptica path, each of said driving means including a driven rod for communicating motion to the associated element, an-c means to vary the inclination of the maj or axis of the elliptical path of said other driving means relative to the axis of movement of the associated element.

3. A pump comprising a piston and a cylinder, means to separately reciprocate said piston and cylinder synchronously and variably relative to each other, comprising an eccentrically driven shaft, a link rotatably journalled upon said shaft and connected to said piston, an eccentric cam rotatably journalled upon said shaft and connected to said cylinder, means operable synchronously with said piston and said cylinder to introduce and effect a discharge of a fluid from the. cylinder, comprising valves for said cylinder.

4. A pump comprising a cylinder element and a piston element therein, means to separately reciprocate the said elements synchronously and variably relative to each other, comprisin an eccentrically driven shaft, a

link rotatably journalled on said shaft and connected to one of the elements, an eccentric cam rotatably journalled on the shaft and a cam follower link on the cam and connected to the other element, and means for shifting the rotary position of the eccentric cam relative to its link to vary the phase relation of the reciprocatory movement of said other element.

5. A pump comprising a cylinder element and a piston element therein, means to separately reciprocate said piston element and cylinder element synchronously and variably relative to each other, the means for reciprocating one of said elements comprising an eccentrically driven shaft, an eccentric cam rotatably journalled on the shaft, a cam follower link on the cam and connected to said element and means for adjustably changing the rotary position of the. eccentric cam to vary the phase relationship of the reciprocations of said elements, said means comprising a link pivoted at one end to the eccentric cam and supported on a stationary pivot at its other end.

6. A pump comprising a cylinder element and a piston element therein, means to sepa rately reciprocate said piston element and cylinder element synchronously and variably relative to each other. the means for reciprocating one of said elements comprising an eccentrically driven shaft, an eccentric cam rotatably ournalled on the shaft, a cam follower link on the cam and connected to said element, means for adjustably changing the rotary position of the eccentric cam to vary the phase relationship of the reciprocations of said elements, said means comprising a link pivoted at one end to the eccentric cam and supported on a stationary pivot at its other end, and means to adjustably snift the stationary pivot.

7. A. pump comprising a cylinder element and a piston element therein, means to separately reciprocate said piston element and cylinder element synchronously and variably relative to each other, comprising aneccentrically driven shaft, a link rotatably journalled on said shaft and connected to one of said elements, an eccentric cam rotatably journalled on said shaft and a cam follower link on the cam and connected to the other of said elements, means operable synchronously with said piston and cylinder elements to introduce and effect a discharge of a fluid 10 from the cylinder element comprising valves .lor said cylinder element.

In testimony whereof I hereunto afiix my signature this 5th day of December, 1928.

1 CRAWFORD B. SANDERS. 

